US9650980B2 - Method and device for controlling a valve - Google Patents
Method and device for controlling a valve Download PDFInfo
- Publication number
- US9650980B2 US9650980B2 US14/434,654 US201314434654A US9650980B2 US 9650980 B2 US9650980 B2 US 9650980B2 US 201314434654 A US201314434654 A US 201314434654A US 9650980 B2 US9650980 B2 US 9650980B2
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- time period
- current
- actuator
- valve
- control voltage
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
- F02D41/2406—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using essentially read only memories
- F02D41/2425—Particular ways of programming the data
- F02D41/2429—Methods of calibrating or learning
- F02D41/2451—Methods of calibrating or learning characterised by what is learned or calibrated
- F02D41/2464—Characteristics of actuators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
- F02D41/2406—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using essentially read only memories
- F02D41/2425—Particular ways of programming the data
- F02D41/2429—Methods of calibrating or learning
- F02D41/2438—Active learning methods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
- F02D41/2406—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using essentially read only memories
- F02D41/2425—Particular ways of programming the data
- F02D41/2429—Methods of calibrating or learning
- F02D41/2441—Methods of calibrating or learning characterised by the learning conditions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
- F02D41/2406—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using essentially read only memories
- F02D41/2425—Particular ways of programming the data
- F02D41/2429—Methods of calibrating or learning
- F02D41/2451—Methods of calibrating or learning characterised by what is learned or calibrated
- F02D41/2464—Characteristics of actuators
- F02D41/2467—Characteristics of actuators for injectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/3809—Common rail control systems
- F02D41/3836—Controlling the fuel pressure
- F02D41/3863—Controlling the fuel pressure by controlling the flow out of the common rail, e.g. using pressure relief valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
- F02M59/368—Pump inlet valves being closed when actuated
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
- F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
- F02D2041/2024—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit the control switching a load after time-on and time-off pulses
- F02D2041/2027—Control of the current by pulse width modulation or duty cycle control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
- F02D2041/2041—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit for controlling the current in the free-wheeling phase
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
- F02D41/2406—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using essentially read only memories
- F02D41/2425—Particular ways of programming the data
- F02D41/2429—Methods of calibrating or learning
Definitions
- the invention relates to a method and a device for controlling a valve.
- a valve of this kind is used, for example, in a high-pressure pump for delivering fluid for an accumulator-type injection system for internal combustion engines of motor vehicles.
- Valves of this kind are subjected to intense stresses, in particular if they are subjected to continuous loading such as is the case in high-pressure pumps for example. Since high-pressure pumps are subjected to pressures of, for example, 2000 bar and more in diesel internal combustion engines, high demands are placed on the valves in pumps of this kind.
- One embodiment provides a method for controlling a valve which has a spring with a spring force and an actuator with an actuator force which counteracts the spring force, in which method for the purpose of closing the valve in a predefined first operating mode, a predefined starting voltage is applied to the actuator, a maximum current value is determined, said maximum current value representing a current peak of a current which is impressed by the applied starting voltage, a first time period is determined, said first time period being representative of the time which has passed between the starting voltage being applied and the maximum current value being reached, a minimum current value is determined, said minimum current value representing a local minimum of the impressed current, wherein the minimum current value follows the maximum current value, a second time period is determined, said second time period being representative of the time which has passed between the starting voltage being applied and the minimum current value being reached, for the purpose of closing the valve in a predefined second operating mode, the predefined starting voltage is applied to the actuator, specifically for the determined first time period, and then, after the first time period until the end of the second time period, the current which
- control voltage is determined depending on the determined first time period and/or on the determined second time period.
- the current of the actuator is adjusted by means of the control voltage, after the first time period until the end of the second time period, in such a way that it corresponds approximately to a predefined lower limit value at the end of the second time period.
- the current is adjusted by means of a freewheeling phase after the first time period until the end of the second time period, the control voltage being zero and the current being adjusted by a freewheel in said freewheeling phase.
- control voltage is adjusted by means of pulse-width modulation after the first time period until the end of the second time period.
- valve is arranged in a high-pressure pump in the form of an inlet valve.
- Another embodiment provides a device for controlling a valve which has a spring with a spring force and an actuator with an actuator force which counteracts the spring force, wherein the device is designed to: determine a maximum current value which represents a current peak of a current which is impressed by an applied starting voltage, determine a first time period which is representative of the time which has passed between the starting voltage being applied and the maximum current value being reached, determine a minimum current value which represents a local minimum of the impressed current, wherein the minimum current value follows the maximum current value, determine a second time period which is representative of the time which has passed between the starting voltage being applied and the minimum current value being reached, and apply the predefined starting voltage to the actuator, specifically for the determined first time period, and then, after the first time period until the end of the second time period, adjust the current which is impressed onto the actuator by means of a predefined control voltage, wherein the average value of the control voltage is lower than the average value of the starting voltage.
- FIG. 1 shows a longitudinal section through a pump having a valve
- FIG. 2 shows a longitudinal section through the valve
- FIG. 3 a shows a current profile during control of the valve
- FIG. 3 b shows a further current profile during control of the valve
- FIG. 4 a shows a further current profile during control of the valve
- FIG. 4 b shows a further current profile during control of the valve
- FIG. 5 shows a circuit diagram
- Embodiments of the invention provide a method and a corresponding device that permit precise operation of a valve.
- Some embodiments provide a method and by a corresponding device for controlling a valve.
- the valve has a spring with a spring force and an actuator with an actuator force which counteracts the spring force.
- a predefined starting voltage is applied to the actuator for the purpose of closing the valve.
- a maximum current value is also determined, said maximum current value representing a current peak of a current which is impressed by the applied starting voltage.
- a first time period is determined, said first time period being representative of the time which has passed between the starting voltage being applied and the maximum current value being reached.
- a minimum current value is determined, said minimum current value representing a local minimum of the impressed current. The minimum current value follows the maximum current value.
- a second time period is determined, said second time period being representative of the time which has passed between the starting voltage being applied and the minimum current value being reached.
- the predefined starting voltage is applied to the actuator for the purpose of closing the valve.
- the starting voltage is applied for the determined first time period.
- the current which is impressed onto the actuator is adjusted by means of a predefined control voltage.
- the average value of the control voltage is lower than the average value of the starting voltage.
- Important information for the valve such as the closing period of the valve for example, is obtained in the first operating mode. This information is used in order to drive the valve in the second operating mode. As a result, it is possible for the valve to be precisely driven.
- the power consumption by the valve may possibly be reduced compared to conventional driving, and as a result the service life of the valve may increase and further positive side effects, such as reduced noise production by the valve during closing, may possibly additionally be achieved too.
- control voltage is determined depending on the determined first time period and/or on the determined second time period.
- the current which is impressed onto the actuator is adjusted by means of the control voltage, after the first time period until the end of the second time period, in such a way that it corresponds approximately to a predefined lower limit value at the end of the second time period.
- the lower limit value is a value at which it is possible to ensure that the valve is closed. As a result, the power consumption may possibly be reduced.
- the impressed current is adjusted by means of a freewheeling phase after the first time period until the end of the second time period, the control voltage being zero in said freewheeling phase and the current being adjusted by a freewheel in said freewheeling phase.
- control voltage is adjusted by means of pulse-width modulation after the first time period until the end of the second time period.
- valve is arranged in a high-pressure pump in the form of an inlet valve.
- FIG. 1 shows a pump 10 having a pump housing 12 .
- the pump 10 is in the form of a high-pressure pump in particular, preferably in the form of a radial piston pump.
- a pump piston 14 is movably mounted in the pump housing 12 .
- a pressure chamber 16 is located at one end of the pump piston 14 in the pump housing 12 .
- said pressure chamber has an inflow line 18 in which a valve 20 , which is in the form of an inlet valve, is preferably arranged.
- the valve 20 is preferably in the form of a digitally switched valve.
- the valve 20 facilitates filling of the pressure chamber 16 and prevents the fluid from flowing back out of the inflow line 18 during filling.
- the pressure chamber 16 further has an outflow line 22 in which a further valve 24 , which is in the form of an outlet valve, is arranged. Therefore, fluid can be expelled from the pressure chamber 16 .
- the pump 10 further has a drive shaft 26 which is operatively connected to a cam-like body 28 which predefines a cam-like profile to the pump piston 14 and can be rotated, for example clockwise, in a rotation direction D.
- a cam-like body 28 which predefines a cam-like profile to the pump piston 14 and can be rotated, for example clockwise, in a rotation direction D.
- an eccentric ring or a camshaft can also be used for example, and, as an alternative, the pump 10 can also be designed as a crank drive pump.
- FIG. 2 shows the valve 20 having a valve housing 29 which has a recess 30 .
- a spring 32 , a pin 34 and a sealing element 36 are arranged in the recess 30 .
- the spring 32 is arranged between a wall of the recess 30 and the pin 34 .
- a spring force F_ 1 which is generated by the spring 32 , acts on the pin 34 , as a result of which the sealing element 36 is prestressed by means of the pin 34 .
- the pin 34 has a first cylindrical part 34 a and a second cylindrical part 34 b , wherein the first part 34 a has a larger diameter than the second part 34 b.
- the recess 30 further contains a sealing seat 38 which is fixedly arranged with respect to the valve housing 29 and which has cutouts 40 . Fluid can flow via the cutouts 40 if the sealing element 36 is not bearing against the sealing seat 38 .
- the pump piston 14 is moved toward the drive shaft 26 by means of the cam-like body 28 until said pump piston reaches a bottom dead center.
- the pressure in the pressure chamber 36 is reduced as a result of this movement. This results in a change in the forces which act on the valve and the valve 20 ultimately opens on account of the spring force F_ 1 of the spring 32 and the pressure difference between the inflow line 18 and the pressure chamber 36 .
- the sealing element 36 lifts away from the sealing seat 38 . This time at which the sealing element 36 lifts away from the sealing seat 38 is called the natural opening time.
- an actuator force F_ 2 which counteracts the spring force F_ 1 , acts on the pin 34 as a result of a voltage being applied to the actuator 42 .
- the pin 34 moves in the direction of the actuator force F_ 2 on account of the actuator force F_ 2 and the pressure difference between the pressure chamber 36 and the inflow line 18 .
- valve 20 is closed in this way.
- the fluid which is compressed in the pressure chamber 16 can now be fully expelled from the pump 10 via the further valve 24 , which is in the form of an outlet valve.
- the pump 10 is a high-pressure fuel pump of an injection system of an internal combustion engine
- the fuel which is subjected to the high pressure can be passed to a fluid reservoir which is in the form of a high-pressure fuel reservoir, the so-called common rail.
- Control of the valve 20 for a normally open valve will be illustrated in detail below ( FIG. 3 a , FIG. 4 a , FIG. 3 b , FIG. 4 b ). It goes without saying that this can be applied to a normally closed valve in a corresponding manner.
- a predefined starting voltage is applied to the actuator 42 in order to close the valve ( FIG. 3 a , FIG. 4 a ).
- the first operating mode MP is, for example, a measurement mode which takes place, for example, in an overrun phase.
- the predefined starting voltage is, for example, the battery voltage, or a voltage which is set, for example, by pulse-width modulation.
- a current is impressed onto the actuator 42 by the starting voltage.
- a maximum current value MAX is determined, said maximum current value representing a current peak of the impressed current.
- a first time period T 1 is determined, said first time period being representative of the time which has passed between the starting voltage being applied and the maximum current value MAX being reached.
- a minimum current value MIN is determined, said minimum current value representing a local minimum of the impressed current, wherein the minimum current value MIN follows the maximum current value MAX.
- a second time period T 2 is determined, said second time period being representative of the time which has passed between the starting voltage being applied and the minimum current value MIN being reached.
- the first time period T 1 and the second time period T 2 can be used to obtain important information about the valve 20 , for example it is possible to determine whether the valve 20 is closing slowly or quickly.
- a predefined second operating mode AP the predefined starting voltage is applied to the actuator 42 for the first determined time period T 1 ( FIG. 3 b , FIG. 4 b ).
- the second operating mode AP is, for example, an application mode.
- the current which is impressed onto the actuator 42 is adjusted by means of a predefined control voltage.
- the control voltage is adjusted such that the average value of the control voltage is lower than the average value of the starting voltage.
- the control voltage is determined depending on the first time period T 1 and/or the second time period T 2 .
- the control voltage is adjusted depending on the magnitude of the difference between the second time period T 2 and the first time period T 1 such that it is higher, for example, for a larger magnitude than for a smaller magnitude.
- control voltage can be adjusted by means of a freewheeling phase, the control voltage being zero in this freewheeling phase and the current being adjusted by a freewheel, such as in FIG. 5 by means of a freewheeling diode FL and a switch SW for example.
- a control voltage of greater than zero it is possible to apply to the valve 20 , said control voltage being adjusted by means of pulse-width modulation for example. Specifically for slow valves 20 , it may be necessary to apply a control voltage of greater than zero.
- the current value correspond approximately to a predefined lower limit value U_GW.
- the lower limit value U_GW is, for example, a determined value at which it is ensured that the valve is closed. Therefore, it is possible, for example, for the control voltage to be adjusted such that the current which is impressed onto the actuator 42 drops until it reaches the lower limit value U_GW.
- the current can first be lowered with the freewheeling phase and then with a control voltage greater than zero.
- the control voltage is, for example, a pulse-width-modulated voltage. Since the voltage peaks can be just as high as, for example, the starting voltage in the case of pulse-width modulation, the average value of at least one range of the control voltage is relevant in this respect with regard to the resulting actuator force, in order to compare the control voltage with the starting voltage. The same applies if, for example, the starting voltage is pulse-width modulated, and therefore an average value is also relevant in the case of said starting voltage.
- a so-called holding mode typically follows after the second time period T 2 has elapsed. In the holding mode, it is ensured that the valve 20 is closed and remains closed. To this end, the current is kept at a low level, for example, by means of a two-point controller.
- valve 20 It is possible to reduce the energy consumption by the valve 20 by driving in the second operating mode AP, for example the application mode. Unnecessary heating of the valve 20 can be avoided as a result.
- the coil service life of the valve 20 may be extended and the CO2 emissions may be reduced in this way.
- the reduction of power in the period after the first time period has elapsed and until the second time period T 2 has elapsed may possibly also ensure that noise is minimized.
- information about the closing period of the valve 20 can be determined depending on the first time period T 1 and the second time period T 2 and precise pump control can be achieved as a result since quick valves 20 may have to be driven by a controller at a later time and/or slower valves 20 may have to be driven by the controller at an earlier time.
- diagnosis for example of the degree of wear, or analysis of the valve 20 is possible by the first defined operating mode MP.
- a production spread of individual valves 20 can, for example, also be compensated for by targeted driving on account of the determined first time period T 1 and second time period T 2 .
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Magnetically Actuated Valves (AREA)
- Fuel-Injection Apparatus (AREA)
- Power Engineering (AREA)
Abstract
Description
Claims (12)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
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DE102012218370 | 2012-10-09 | ||
DE102012218370.1 | 2012-10-09 | ||
DE102012218370.1A DE102012218370B4 (en) | 2012-10-09 | 2012-10-09 | Method and device for controlling a valve |
PCT/EP2013/070703 WO2014056797A1 (en) | 2012-10-09 | 2013-10-04 | Method and device for controlling a valve |
Publications (2)
Publication Number | Publication Date |
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US20150263648A1 US20150263648A1 (en) | 2015-09-17 |
US9650980B2 true US9650980B2 (en) | 2017-05-16 |
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Application Number | Title | Priority Date | Filing Date |
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US14/434,654 Active 2033-10-20 US9650980B2 (en) | 2012-10-09 | 2013-10-04 | Method and device for controlling a valve |
Country Status (5)
Country | Link |
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US (1) | US9650980B2 (en) |
KR (1) | KR102069928B1 (en) |
CN (1) | CN104685193B (en) |
DE (1) | DE102012218370B4 (en) |
WO (1) | WO2014056797A1 (en) |
Cited By (1)
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US11217407B2 (en) * | 2017-09-26 | 2022-01-04 | Abb Schweiz Ag | Method for operating a medium voltage circuit breaker or recloser and medium voltage circuit breaker or recloser itself |
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DE102012218370B4 (en) | 2012-10-09 | 2015-04-02 | Continental Automotive Gmbh | Method and device for controlling a valve |
DE102013220407B4 (en) * | 2013-10-10 | 2022-09-29 | Vitesco Technologies GmbH | Method and device for operating an injection valve |
DE102014203364B4 (en) * | 2014-02-25 | 2023-03-23 | Vitesco Technologies GmbH | Method and device for operating a valve, in particular for an accumulator injection system |
JP6432471B2 (en) * | 2015-09-08 | 2018-12-05 | 株式会社デンソー | High pressure fuel pump solenoid valve control device and high pressure fuel pump solenoid valve control method |
DE102016201894A1 (en) * | 2016-02-09 | 2017-08-24 | Robert Bosch Gmbh | Method for controlling an electromagnetic actuator |
DE102016219956B3 (en) * | 2016-10-13 | 2017-08-17 | Continental Automotive Gmbh | Method for adjusting a damping flow of an intake valve of a motor vehicle high-pressure injection system, and control device, high-pressure injection system and motor vehicle |
EP4073391A2 (en) * | 2019-12-12 | 2022-10-19 | Danfoss Power Solutions II Technology A/S | System and method for solenoid valve optimization and measurement of response deterioration |
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WO2014056797A1 (en) | 2014-04-17 |
CN104685193B (en) | 2017-09-08 |
DE102012218370B4 (en) | 2015-04-02 |
US20150263648A1 (en) | 2015-09-17 |
KR20150064074A (en) | 2015-06-10 |
CN104685193A (en) | 2015-06-03 |
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DE102012218370A1 (en) | 2014-04-10 |
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